CN116075650A

CN116075650A - Friction element for a friction working device

Info

Publication number: CN116075650A
Application number: CN202180056792.2A
Authority: CN
Inventors: 克里斯汀·腾达
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2020-08-11
Filing date: 2021-07-06
Publication date: 2023-05-05
Also published as: JP2023538004A; US20240183407A1; WO2022033625A1; DE102021117365A1

Abstract

The invention relates to a friction part (15) for a friction working device, which friction part has friction lining elements (31-33) with grooves (34, 35) arranged between them in order to form a friction surface (16) in the form of a disk, the grooves being traversed by a coolant and/or lubricant in a radial direction relative to the friction surface (16) from radially inside to radially outside, in which case resistance losses occur and air is sucked in together with the coolant and/or lubricant. In order to functionally improve the friction element (16), the configuration of the friction lining elements (31-33) and the arrangement of the friction lining elements (31-33) relative to each other are optimized while taking into account the interdependence between the intake of air and the separation behavior of the friction working means relative to the loss of resistance.

Description

Friction element for a friction working device

Technical Field

The invention relates to a friction part for a friction working device, which friction part has friction lining elements with grooves arranged between them in order to form a friction surface in the form of a disk, which grooves can be traversed by a coolant and/or lubricant in a radial direction relative to the friction surface from the radially inner side to the radially outer side, in which case a loss of resistance occurs and air is sucked in together with the coolant and/or lubricant.

Background

The friction lining element is also referred to as a friction segment, friction lining segment or pad. The friction lining element is preferably attached to the lining carrier on both sides. By the configuration, size and arrangement of the friction lining elements, a variety of groove patterns may be formed. For example, reference is made to EP 0 625 647 B1, EP 2 066

911B1, US 5,094,331 and US 5,335,765.

Disclosure of Invention

The object of the present invention is to improve the function of a friction element according to the preamble of claim 1, in particular for a wet-running clutch or brake, in particular for a wet-running multi-disc clutch or brake.

This object is achieved by a friction part for a friction working device, which friction part has friction lining elements arranged with grooves between them in order to form a friction surface in the form of a disk, the coolant and/or lubricant being able to traverse the grooves in a radial direction relative to the friction surface from the radially inner side to the radially outer side, in which case a drag loss occurs and air is sucked in together with the coolant and/or lubricant, characterized in that the configuration of the friction lining elements and the arrangement of the friction lining elements relative to each other are optimized while taking into account the interdependence between the suction of air and the separation behavior of the friction working device relative to the drag loss. The undesired loss of resistance preferably occurs in the open state of a friction working device equipped with friction members, in particular several friction members. As the demand increases, particularly in connection with new drive concepts, it is important to minimize drag losses. Various groove patterns are proposed for the claimed friction component, with which the pressure level and pressure distribution in the lubrication gap or groove is minimized. In particular, the causality of the intake and/or separation behaviour of air and its effect on the loss of resistance is considered.

A preferred exemplary embodiment of the friction part is characterized in that the friction lining elements are designed and spaced apart relative to one another in such a way that the radial grooves extend in a diffuser-like manner from the radially inner side to the radially outer side in relation to the friction surface. In this way, the pressure in the groove may be reduced during operation of the friction working device. This advantageously shifts the intake of air to lower engine speeds.

A further preferred exemplary embodiment of the friction part is characterized in that the friction lining elements are designed and spaced apart from one another in such a way that the radial grooves narrow in a nozzle-like manner from the radially inner side to the radially outer side in relation to the friction surface. This causes the pressure in the tank to increase. Thus, in the open state of the friction working means, an even distribution of the gaps can be produced.

In another exemplary embodiment, two exemplary embodiments having a diffuser-like extension and a nozzle-like narrowing are combined with each other in the friction member. The exemplary embodiment may, for example, alternate in the circumferential direction in sections of the friction surface.

A further preferred embodiment of the friction part is characterized in that at least two friction lining elements adjacent in the circumferential direction with respect to the friction surface have a slope facing each other on the radially inner side in order to form a kind of funnel at the beginning of the radial groove provided between adjacent friction lining elements. In the closed state of the friction working means, a lubricating wedge is thus created which supports the separation when opened. Furthermore, a gentle closing of the friction working means is possible. The radial grooves adjacent in the circumferential direction are particularly advantageously not equipped with a funnel at the beginning. Thereby, the risk of the friction member undesirably floating when the friction working means is closed can be reduced.

A further preferred embodiment of the friction part is characterized in that at least two friction lining elements adjacent in the circumferential direction with respect to the friction surface have a chamfer facing each other on a radially outer side in order to form a kind of funnel at the ends of the radial grooves provided between adjacent friction lining elements. Thereby, the intake of air can be improved by a slight reduction of the frictional contact area, in particular the surface pressure.

A further preferred exemplary embodiment of the friction element is characterized in that the friction lining element has the configuration of an isosceles trapezoid or preferably has the configuration of an acute triangle. With such a friction lining element or friction lining pad, the desired effect can be further optimized.

Another preferred exemplary embodiment of the friction part is characterized in that the radial grooves are connected to each other by tangential grooves, wherein the friction lining elements are separated in the radial direction to form tangential grooves. Increased design and manufacturing complexity is deliberately accepted to produce improved air distribution in the lubrication gap, i.e. in the groove. Adjacent tangential slots are advantageously offset from each other in the radial direction. Thereby, wear during operation of the friction working means can be minimized.

Another preferred exemplary embodiment of the friction element is characterized in that the friction lining element has a recess on the radially outer side and/or the radially inner side with respect to the friction surface, which recess serves to form an additional blind groove. The blind grooves on the outer diameter create dead spots in the media flow, which improves air intake and reduces drag torque. Blind grooves on the inner diameter of the friction surface accumulate media in the lubrication gap or groove and improve separation of the friction surface. In the closed state, the blind slots improve the cooling effect of the medium, since the convection transitions in the blind slots are improved.

Another preferred exemplary embodiment of the friction element is characterized in that the recess has a rectangular configuration, which is rounded off at the blind groove end. This has proven to be advantageous for undesired floating of the friction member.

The invention also relates to a wet-running clutch or brake, in particular a wet-running multi-disc clutch or brake, having at least one friction element as described above. Several friction elements are advantageously arranged between the two steel discs of the disc clutch or disc brake. Wet running clutches are designed as single clutches or dual clutches. Wet running clutches or brakes are particularly preferred in hybrid modules or when combined with switchable electrically driven bridges.

Drawings

Other advantages, features and details of the present invention will become apparent from the following description, wherein various exemplary embodiments are described in detail with reference to the drawings. In the drawings:

FIG. 1 shows a schematic representation of a half section of a friction working device designed as a wet-running multi-disc clutch;

fig. 2 shows three cartesian diagrams, in which the volume flow, the gap filling level and the resistance torque are plotted against the rotational speed of the friction working device of fig. 1, respectively;

FIG. 3 shows a Cartesian graph with an improved drag torque curve as a function of rotational speed; and

fig. 4 to 12 each show a schematic cross-sectional view of a friction part with friction lining elements of different designs and arrangements in plan view.

Detailed Description

In fig. 1, a half section of a friction working device designed as a wet-running multi-disc clutch 1 is schematically shown. The wet-running multi-disc clutch 1 includes an inner disc carrier 2 and an outer disc carrier 3. The two

disc carriers

2, 3 can be rotated relative to each other about the rotation axis 4 at different rotation speeds independently of each other, which is indicated by

arrows

5, 6.

The disc pack of the wet running multi-disc clutch 1 includes steel discs 7 and lined discs 8. The padded disks 8 each comprise a pad carrier 9 which is connected to the inner disk carrier 2 on the radially inner side of the coupling region 10 in a rotationally fixed manner. The coupling region 10 of the brake pad carrier 9 is designed, for example, as an internal toothing, which meshes with a complementary external toothing of the inner disc carrier 2. Similarly, the steel disc 7 is connected to the outer disc carrier 3 radially outside in a rotationally fixed manner.

The friction linings 11, 12 are fastened on both sides of the lining carrier 9, i.e. on the left and right in fig. 1. The design and function of the wet-running multi-disc clutch 1 is known per se and will not be explained further here. Arrow 13 represents the cooling and/or lubricating medium which enters the disk stack of the wet disk clutch 1 radially on the inside through the inner disk carrier 2. Arrow 14 indicates that the cooling and/or lubricating medium leaves the outer disc carrier 3 radially outside.

The cooling and/or lubricating medium is mainly used for cooling in the wet-running disk clutch 1. The lining disk 8 with the lining carrier 9 and the two

friction linings

11, 12 is also referred to as a friction element 15. The friction member 15 has a friction surface 16 facing the steel disk 7 as shown on the right side in fig. 1.

The friction surface 16 is radially inward defined by an inner radius r _i And (5) delimitation. The friction surface 16 is radially outwardly formed by an outer radius r _a And (5) delimitation. On the left side of fig. 1, the friction portion 15 comprises a further friction surface facing the adjacent steel disc, which is not shown in further detail. In order to transmit torque, the friction member 15 can be clamped with its annular disc-shaped friction surface 16 between two adjacent steel discs 7 in each case.

In fig. 2, three cartesian graphs are shown, one above the other. The rotational speed during operation of the wet running multi-plate clutch 1 with friction member 15 is plotted on the x-axis 20 in appropriate units. The volumetric flow is plotted on the y-axis 21 in appropriate units. The gap fill level is plotted on the y-axis 22 in appropriate units. The drag torque is plotted on the y-axis 23 in appropriate units.

Fig. 2 illustrates how air is sucked 26 through the sucked volume flow 24 when the sucked volume flow exceeds the supplied volume flow 25. From this limit, the gap fill level 26 decreases and the lubrication gap between the disks contains air. Beyond this limit, the supplied volumetric flow 25 contains air. The bottom of fig. 2 shows that the suction 26 of air occurs at the maximum resistance torque 27.

Fig. 3 shows how the displacement of the suction 28 of air in the drag torque curve 30 to a low rotational speed is achieved with the claimed friction member 15. The conveying effect of the cooling and/or lubricating medium can be improved by the groove pattern shown in fig. 4 to 12.

In each of fig. 4 to 12, a portion of the friction surface 16 of the friction member 15 of fig. 1 is schematically shown in a plan view. The inner diameter of the friction surface 16 is denoted by Di. The outer diameter of the friction surface 16 is denoted by Da.

The friction member 15 shown in fig. 4 includes three friction lining elements 31 to 33 in the shown portion of the friction surface 16. The friction lining elements or friction lining pads 31 to 33 have a configuration of an isosceles trapezoid whose size in the circumferential direction decreases from the inner diameter Di to the outer diameter Da of the friction surface 16.

Thus, the

radial grooves

34, 35 between the

friction lining elements

31, 32 and between 32, 33 extend in a diffuser-like manner from the radially inner side to the radially outer side. Thereby, an additional pressure reduction is created in the

grooves

34, 35. In this way, the intake of air (28 in fig. 3) can be diverted towards a low rotational speed. This significantly reduces the drag torque (30 in fig. 3).

In the exemplary embodiment illustrated in fig. 5,

tangential grooves

37, 38, 39 are provided in addition to

radial grooves

34, 35. The friction lining elements 31 to 33 are interrupted to show tangential grooves 37 to 39.

The additional tangential grooves 37 to 39 improve the air distribution in the grooves, which are also referred to as lubrication gaps as a whole. In order not to deteriorate the contact pattern in the friction surface 16, the tangential grooves 38 are offset radially inwards in relation to the

tangential grooves

37, 39 in the radial direction.

Fig. 6 shows that the trapezoidal friction lining elements 31 to 33 shown in fig. 4 can also be replaced in the extreme case by triangular friction lining elements 41 to 43. The

radial slots

44, 45 thus created extend radially outwardly more than in fig. 4. In contrast to what is shown, the

grooves

44 and 45 in fig. 6 can also be combined with tangential grooves (37 to 39 in fig. 5).

Fig. 7 shows that the triangular friction lining elements 47 to 49 may also be arranged in a manner opposite to that in fig. 6, with their tips being radially inward. The

radial grooves

50, 51 thus produced narrow in a nozzle-like manner from the radially inner side to the radially outer side. The narrowing nozzle-like groove cross section on the outer diameter Da of the friction surface 16 generates a pressure increase in the lubrication gap.

This may result in an improved separation behaviour of the carrier disc if there are no corrugations in the disc. In the open state of the multi-plate clutch 1, the drag torque can be effectively reduced by the optimum plate distribution.

The embodiment shown in fig. 8 is similar to the embodiment shown in fig. 4. The

friction lining elements

53, 54, 55 are each provided with two

bevels

56, 57 on the outer diameter Da; 58. 59; 60. 61.

Radial grooves

61, 62 formed between the friction lining elements 53 to 55 are

inclined surfaces

57, 58 on the outer diameter Da of the friction surface 16 in a funnel-like manner; 59. 60 extends in the region of the base. This improves the intake of air with a slight reduction in the frictional contact area.

Fig. 9 shows that

friction lining elements

64, 65, 66 may also be provided with

bevels

67, 68, 69 on the inner diameter Di of friction surface 16. The

bevels

67, 68 of the

friction lining elements

64, 65 face each other such that the radial groove 70 formed between the

friction lining elements

64, 65 extends over the inner diameter Di in a funnel-shaped configuration. On the other hand, the radial groove 71 between the

friction lining elements

65, 66 is designed without a bevel.

The groove 70 with a funnel-shaped extension on the inner diameter Di creates a lubrication wedge when the multi-plate clutch 1 is closed and supports the separation of the plates when open. The groove 71 without a bevel helps to reduce the risk of the friction member 15 floating when closed. Thus, the radial grooves 71 help ensure that the multi-plate clutch 1 is smoothly closed.

In fig. 10 to 12, the three rectangular

friction lining elements

73, 74, 75 are spaced apart from one another in the circumferential direction, so that

radial grooves

76, 77 are formed. The friction lining elements 73 to 75 are provided with recesses on the outer diameter Da in fig. 10, on the inner diameter Di in fig. 11, and on both the inner diameter Di and the outer diameter Da in fig. 12, so as to form

blind grooves

78, 79, 80;81 to 86.

Blind slots 78 to 80 in fig. 10 open radially outward. Blind slots 78 to 80 in fig. 11 are open on the radially inner side. The blind slots 81 to 83 in fig. 12 are also open on the radially inner side. Blind slots 84 to 86 in fig. 12 open radially outward.

With the blind grooves 78 to 80 on the outer diameter Da in fig. 10 and the blind grooves 84 to 86 on the outer diameter Da in fig. 12, dead spots with corresponding pressure reduction are produced in the medium flow. This improves air intake and results in reduced drag torque.

The blind grooves 78 to 80 on the inner diameter Di in fig. 11 and the blind grooves 81 to 83 on the inner diameter Di in fig. 12 cause the medium to accumulate in the lubrication gap. This results in an improved separation behaviour. At the same time, the cooling effect of the medium is improved when the multiplate clutch 1 is in the closed state, because the convective heat transfer in the blind grooves is improved.

List of reference numerals

1. Wet running type multi-disc clutch

2. Internal multi-disc carrier

3. External multi-disc carrier

4. Axis of rotation

5. Rotational speed

6. Rotational speed

7. Steel disc

8. Disk with lining

9. Lining carrier

10. Coupling region

11. Friction lining

12. Friction lining

13. Arrows

14. Arrows

15. Friction member

16. Friction surface

20 X-axis

21 Y-axis

22 Y-axis

23 Y-axis

24. Volumetric flow rate of inhalation

25. Volume flow rate of supply

26. Air intake

27. Resistance torque

28. Air intake

30. Resistance torque curve

31. Friction lining element

32. Friction lining element

33. Friction lining element

34. Groove(s)

35. Groove(s)

37. Tangential groove

38. Tangential groove

39. Tangential groove

41. Friction lining element

42. Friction lining element

43. Friction lining element

44. Groove(s)

45. Groove(s)

47. Friction lining element

48. Friction lining element

49. Friction lining element

50. Groove(s)

51. Groove(s)

53. Friction lining element

54. Friction lining element

55. Friction lining element

56. Inclined plane

57. Inclined plane

58. Inclined plane

59. Inclined plane

60. Inclined plane

61. Groove(s)

62. Groove(s)

64. Friction lining element

65. Friction lining element

66. Friction lining element

67. Inclined plane

68. Inclined plane

69. Inclined plane

70. Groove(s)

71. Groove(s)

73. Friction lining element

74. Friction lining element

75. Friction lining element

76. Groove(s)

77. Groove(s)

78. Blind groove

79. Blind groove

80. Blind groove

81. Blind groove

82. Blind groove

83. Blind groove

84. Blind groove

85. Blind groove

86. Blind grooves.

Claims

1. A friction component (15) for a friction working device, which friction component has friction lining elements (31-33; 41-43;47-49;52-55;64-66; 73-75) with grooves (34, 35;44, 45;50, 51;61, 62; 70; 71;76, 77) arranged therebetween so as to form a friction surface (16) in the form of a disk, a coolant and/or lubricant being able to traverse the grooves from radially inside to radially outside in relation to the friction surface (16), in which case a loss of resistance occurs and air is sucked in together with the coolant and/or lubricant, characterized in that the configuration of the friction lining elements (31-33; 41-43;47-49;52-55;64-66; 73-75) and the arrangement of the friction lining elements (31-33; 41-43;47-49;52-55;64-66; 73-75) in relation to each other are simultaneously optimised taking into account the mutual loss of resistance between the suction of air and the separation behaviour of the friction working device in relation to the friction working device.

2. A friction part according to claim 1, characterized in that the friction lining elements (31-33; 41-43) are designed and spaced apart opposite to each other in such a way that radial grooves (34, 35;44, 45) extend in a diffuser-like manner in relation to the friction surface (16) from radially inside to radially outside in the radial direction.

3. Friction part according to claim 1, characterized in that the friction lining elements (47-49) are designed and spaced apart opposite to each other in such a way that radial grooves (50, 51) narrow in a nozzle-like manner in relation to the friction surface (16) from radially inside to radially outside in the radial direction.

4. Friction member according to one of the preceding claims, characterized in that at least two friction lining elements (64, 65) adjacent in circumferential direction with respect to the friction surface (16) have on radially inner sides bevels (67, 68) facing each other in order to form a funnel at the beginning of radial grooves (70) provided between adjacent friction lining elements (64, 65).

5. Friction member according to one of the preceding claims, characterized in that at least two friction lining elements (53, 54) adjacent in the circumferential direction with respect to the friction surface (16) have on radially outer sides inclined surfaces (57, 58) facing each other in order to form a funnel at the ends of radial grooves (61) provided between adjacent friction lining elements (53, 54).

6. A friction member according to one of the preceding claims, characterized in that the friction lining element (31-33; 41-43; 47-49) has the configuration of an isosceles trapezoid or preferably has the configuration of an acute triangle.

7. Friction part according to one of the preceding claims, characterized in that the radial grooves (34, 35) are connected to each other by tangential grooves (37-39), wherein the friction lining elements (31-33) are separated in the radial direction to form the tangential grooves (37-39).

8. Friction part according to one of the preceding claims, characterized in that the friction lining element (73-75) has recesses on a radially outer side and/or a radially inner side with respect to the friction surface (16) for forming additional blind grooves (78-80; 81-76).

9. The friction member according to claim 8, wherein the recess has a rectangular configuration, the rectangle being rounded at the blind slot end.

10. Wet-running clutch or brake, in particular wet-running multi-disc clutch (1) or multi-disc brake, having at least one friction element (15) according to one of the preceding claims.